Hydraulic transmission



March 4 {1924; 1,485,986

w. E. MAGIE ET AL V HYDRAULIC TRANSMISSION Original Filed Majrch 25, 1918' '5' Sheets-,Sheet'l v W. E. MAGIE ET AL HYDRAULIC TRANSMISSION March 4 1924 E an March 4, 1924.- 1,485,986 w. E. MAGIE ET AL HYDRAULIC TRANsfiIssIoN Original Filed March 25, 1918 5 sh ets -sheet' WI'TNEZZ? I March 4 1924;

W. E. MAGIE ET AL HYDRAULIC TRANSMISSION 5 sheets sheet 4 Original Filed March 25, 1918 S Illlllll;

J MP/van.

March 4 1924.

w. E. MA'GIE ET AL HYDRAULIC TRANSMISSION Original Filed March 25, 19 18 5 She'ets-Sheet 5 INVENTORS. wzZZ mm 15'. Mag z'e and walterfrrz's ATTORNEY.

Patented-Mar. 4, 1924.

. WILLIAM E. MAGIE, or BurrALo; NEW

WAUZKEE, WISCONSIN,

YORK, AND WALTER reams, or sou'rn AssIeNons-To THE ornemn COMPANY, or MILWAUKEE,

wxs'consm, A coaroaArIo-N OF WISCONSIN.

HYDRAULIC TRANSMISSION.

MIL-

Application filed March 25, 1918, Serial lid 224,503. Renewed August 15, 1921. I Serial, No. 492,460;-

I i I T all whom it may concern Be it known that we, l/ViLLIAM E. MAGIE and ,WAL'rnR FERRIS, citizens of the United Y States; residin respectively, at Buffalo, in the county of Frie and 'State of New York,

and South Milwaukee, in the county of Milwaukee' and State of Wisconsin, have. in-

' vented a certain new and useful Improvementin Hydraulic Transmissions, of. which the following-1s a specification.

Our invention relates to transmission device consisting ofv a pump having variable displacement and a fluid motor operated-by fluid delivered by the. pump; pump and motor comprising groups of cylinders ra dially arranged, as hereinafter described. j

Among the objects of our invention is to reduce the friction of the moving parts and thereby increase the efiiciency; to furnish an improved means of varying the pump displacement; to provide a mechanism with-- out periodical disturbances rate of flow;

'to provide a mechanism in which the total .25

volume'of oil included in the sp'aces'between the'pujmp plungers and the motor plungers remains constant during change in displace-' ment of pump or of motor; to provide a system of ports and valve surfaces whereby the revolvlng; cylinders can receive and d1scharge oil from the stationary co-acting 'parts with a minimum of friction and of leakage; to provide for returning leakage -from'high-pressure system directly into the low pressure ports without requiring the use of a pump amount of mechanism which serve oil, thereby permitting sedimentto be deposited; to provide a fluid powergtransmission mechanism operating with the fluid divided into three zones of pressure and with the moving parts encased in an empty chamber," separated from the reserve reservoir. Other objects of my invention .will appearfrom tilneto time in the specification. 4

Our invention is illustrated more or less diagrammatically in the accompanylng drawings wherein,

fluid to provide an operating substantially'alonqthe line 1 -1 of Figure 2, with, parts broken away; v

a hydraulic power to handle this large and variable.

does not agitate the rev fluid 7 Figure 1 is an end-viewin section taken- Figure 2 is a side elevation'withparts section;

Figure 3 is a deta'ilpn an enlarged scale; Flfllle 4: is a sectional view taken substantially along the line 4-4 with the casing omitted; r

' Figure 5 isasection on an enlarged scale of Figure 2,

of the contact face with the slidingpindleblock'member; 1

Figure 9 is a pressure diagram; Figure 10 is a diagram with he pressure areas; r

Figures 11 and-'12 arediagrammatic views showing relation of pump and motor ends taken on theline R- s of Figure 2';

Figure13 is a view similar to Figure 8: showing pressure areas. I

c Figure 14 is a vertical sectional view of the catch basin taken substantially along the line 14-14 of Figure 1;

17 are diagrammatic views illustrating the function of the roller bearings during operation of the pump "or motor. 1 I l Like parts are indicated by like characters in all the drawings. 4

The pump andidentical."A description of one will sufiice for the other. \Vh'ere in the same drawing we use 9" to indicate the motor end.

, Figures 15, 16 and the exponent synonymous in the power which is to be mechanism. This pump shaft is mounted in bearings A and A* mounted in the endhead A and has keyed to its inner end the driving disc 13 which is cup shaped-and has preferably seven equally spaced flats machilled on the inneripenphery thereof. 110.

both parts are present motor' are substantially The terms oil and working fluid are following description, 4 oil being preferable'on account of 1ts 'adapv each of these flats is secured a hardened steel roller track B, having, gear teeth formed in r the central portion for purposes hereinafter described. In the same transverse plane as the centers of these roller paths, islocated' the central plane of a cylinder barrel C formed with seven equally spaced cylindrical bores. Within each of these bores is a .closely fitting plunger 13 secured to a T' shaped steel crosshead B whose outer sur-' face is provided with a roller path and with car teeth for purposes hereinafter described.

0' Tlungers and crossheads'are held in assembly by a lock pin 13 which fits tightly in the hole shown in crosshead B (Fig. 6) and loosely in corresponding holes through the eration,

lugs on plunger (Fig. 7). This is a retaining pin only and has no function when machine is filled with oil and in normal op- The inner faces of the crossheads B slide upon equally spaced lugs B which are 1ntegral with the web of the driving discs The outer roller path surface of each crosshead engages with the rollers B which rollers also engage the roller pathsB previously described. Each roller bearing assembly comprises a pair of rollers B carried in,

- thereby preventing the roller cage and the rollers B from departing from their proper position with respect to their co-acting parts.

The shanks B of the crossheads B fit closely in the lower endof the bored plungers B the thrust being transmitted from crossheads to plunger through a rocking surface 13 formed at the end of the shank 'B which permits a slight lateral deflection of crossheads with respect .to plungers without any binding action. This lateral deflection is only required in the direction parallel to the axis of the shaft B to compensate for deflections of the driving discs under load, which may act to carry the central plane of roller paths B slightly away from the central plane of cylinder barrel C To accommodate this deflection the diameter of thefiange B which fits the bore as at B 011 opposite sides .permitting the lateral deflec tion of these parts but retainingclose contact with the conical bore of the p'lungers atv the unfiattened areas 30f the flanges B which lie in the central plane of the driving discs. The purpose of this close contact is to maintain at all times equal angular movement of the driving disc B and the cylinder-barrel C which receives. its motion from the driving disc' through-the T- shaped crossheads B and the co-acting plungers B StructurallyB, B and B form a single rigid unit or cross-sliding member having two arms: one being the crosshead arm B preferably at right angles to the other arm which is formed by the shank B and the plunger B The crosshead arms B slide on the crank disc in a tangential di rection,being closely guided by the roller paths B, the rollers B and the lugs B Q Each-plunger engages its corresponding cylinder bore in a radial direction and is closely guided therein. -These co-acting parts form a driving connection between the. driving disc B and the driven cylinder barrel C which compels the cylinder barrel to occupy in all positions during its revolution a con stant angular relation'to the driving disc, I whether the axes of the two rotating bodies are concentric (as when the pump is at zero stroke Fig. 1) or displaced as shown in Figures 11 and 12. It is also true that this same constant angular relation avoids the irregularities in piston travel which occur in mechanisms of this character in which the plungers are operated byuneans of connecting rods; in our arrangement the sum, at

any point in the cycle, of all the distances of the various istons from the extreme in- I ward points of their strokes, is constant;

and thetotal' volume of the liquid enclosed within the cylinders and the communicating passages is constant. Another result is that. the total volume of enclosed liquid does not change when the pump stroke is changed.

The enclosed volume under the pistons and in the communicating passages is constant for all adjustments of the mechanism and for all positions during the cycle, thus at- 1 5,

taining constant non-pulsating flow of the.

working fluid at all times. g

The pump and motor cylinder barrels C and C are each axially bored to receive the pump and motor pintles C and C respectively, upon which they. are .rotatably mounted. Each axial bore constitutes a.

valve chamber having a series of ports C or 0 one for each cylinder bore, cooperating with ports (1 ,0 or C C formed in the supporting pintle above-and below the axis thereof. Although either'or both of the pintles may be adj ustably mounted, the motor pintle C in this instance constitutes an integral part of a stationary cross rail- C The axis of the pintle is permanently offset a distance E (Eigsll and 12) from the axis of the disc B- and shaft B The pump pintle C is formed integral with a P slide block C" mounted on the cross rail C for adjustment.longitudinally thereoff Any appropriate means, such as a screw C threaded in the casing A and having a swivel connection 03 with the block C, may be employed for adjusting and controlling J other andplungers will reciprocate. in and herefore, as these parts revolve together the crossheads' B with attached plungers B revolving with crank disc B maintain a constant distance from the center of pintle C around which the cylinder-barrel is revolving, consequently said'plungers B. will have no stroke in their corresponding pump cylinders, and no oil will bedrawn in or expelled through the cylinder ports C the pum continumgto revolve without displacing any oil.

If the sliding pintle block C X, the driving disc B and the pump cy-v linder barrel C fwill be eccentric to. each out of their respective cylinder bores, each plunger making one double stroke in each' revolution ofthe disc. In the position shown in Fig. 12, the plungers will be at the extreme in-stroke as they pass the horizontal axis on the left ahd at extreme outstroke as they pass the horizontal axis on the right.

The direction of pump rotation is show'nby '1 arrow on Fig. 1; hence during its passage through theupper semi-circleto Fig. 12,. eachplunger is being gradually withdrawn from its cylinder as .it passes from extreme iii-stroke at the left to extreme out-stroke at the-right, thereby taking in a cylinder full of oil from port C As any given cylinder port compe C passes thehorizontal axis at the rightof Fig. 12, it is momentarily closed by the;

bridge C between port C and port-C. Continuing its clockwise movement port C is instantly opened to communicate with'the lower pintle-port G as said'port passes the right hand bridge, and thereafter during its entire half revolution in the lower semicircle the corresponding plunger 13? is m'ov-'- mg radially inward in its cylinder and expelling oil through port G into the lower pintle port C, as hereinafter explained.

This oil is conducted through communicating ports to a similar port-C" and acts againstl similar motor plungers B" thereby 1 C and corresponding motor driving disc B to revolve. The pump plungers as they expel-oil from the lower port C generate,.

in this oil, suflicient pressure toj overcome whatever resistance maybe opposing the revolution of the motor. shaft B If the sliding pintle block 0 be moved to theleft of axis X a less-distance'than E.

ing a similar motorcylinderbarrel' this eccentricity as desired, from zero to a maximum toward the left, as shown in Fig.

12, any desired amountof oil per' unit of time may be transferred by the pump from port C to port C.

Referring to fixed eccentricity of motor-end pintle C" which is formed integral with cross rail 1C.

plunger to take a stroke, equal to twice E.

Fig. 12, E represents the b 4 d i This eccentricity will cause each motor e move a distance E (Fig. 12) to the left of the axis If E, the maximum eccentricity of the P the iiotor,-the cylinder diameters being the same) the pump at full stroke will deliver just enough oil per revolution to operate the motor through one revolution; causing motor to revolve at the same speed as the pump. If the sliding block 0 be moved off center until the eccentricityE is onlyone-quarter of E, four revolutions of the pump will be required to deliver enough oil to turn the motor around once and the speed of the motor will be one-quarter of the full speed. Similarly, any other intermediate motor speeds from zero to maxiis equal to E (the fixed eccentricity of m mum may be obtained byvarying the dis I tance E, Fig. 12. v Fig. 11 indicates the position of the mechanism when sliding block G is moved a' said distance E to the right of axis X,

' fixeddistanceE" being taken equal to the eccentricity E of the motor-pintle C pump cylinder barrel C? posed in this figure upon barrel C the clockwise rotation of the pumpshaft B the plungers will .be at full in-stroke -at the right-hand of Figure 11 and at the the 'motor cylinder C will now become the low pressure or intake port to pump while the oil will be expelled as the cylinders pass around through-the upper semi-circle into port .0 receiving suflicient pressure from the pump-plungers to overcome "the resist? is therefore super-- 4 The n In this condition, continuing full out-stroke at the left hand of said fig- Zure. The lower port ance opposing the revolution of the motors shaft B When the upper port (3 constitutes the high pressure side of the oil circuit, oil passing from plungers B" in the upper half of the path of travel of the motor plungers. As the pintle center-from which these plungers rothis port acts against the 1 tate is to the right ,of the center of the motor driving disc B the radial plunger thrusts act to revolve this disc over to the left or 0pposite to the pumps direction of rotation.

On the other hand, if the high pressure oil is delivered by the pump into the lower port C it will act outward upon the plungers B in the, lower semi-circle and will tend to revolve disc B clockwise, or in the same direction as the pump-disc.

I Communication between the pump-pintle port C and the corresponding inotor-pintle port C is maintained in all positions of the sliding pintle block C by means of two elongated abutting ports C and C formed respectively in the'sliding block CT and the stationary cross rail C Port C is longer than its coriesponding port 6, the addi tional length being the amount E at each end representing the maximum eccentricity of the center of the pump-pintle in either direction from the axis X, Fig. 5.- 'When the pump pintle C is moved to the extreme left-hand position, the right hand end of port C will register with the righthand end of port C thus avoiding any constriction.

',Ifwo similar ports C and W establish com munication between the upper pump-pintle port C and the upper motor-pintle port C During the movement of each cylinder through the semi-circle in communication with thepressure port, a heavy reaction between each crosshead B or B and the coacting driving discs I3 or B is transmitted through the rollers B or 13"" as the crossheads reciprocate. on the track B or B In the case of thepump end, this reaction takes the form of a force. transmitted from the driving disc to the'plungers generating a high pressure in the enclosed liquid which will react against the motor hp ngers. In the case of the motor end, the

reac ion is transmitted through the motor plungers to the driving disc which receives therefrom a driving torque. The rollers B"- and B interposed between the plunger as semblies and their corresponding driving discs reduce friction at these points; substituting for a sliding fricti0n,a very small" amount of rolling friction.

In this connection, it is important, to note that lugs B and B on the pump and motor discs 13 and B respectively, have no function ,during the high pressure'stroke of the mechanism. (The high pressure stroke is the -delivery 1 or inward stroke of the pump plungers, and the driving or outward stroke of the motor plungers.) These-lugs come into action to maintain the assembly .in correctwbelation when there is no pressure 1n the me hanism. In the present case, where nolea age returnpump is used, these lugs also fun ion to draw the pump plungers B outwardly in their cylinders C during the-suction strokes, thus permitting.

the high pressure side of the circuit.

atmospheric pressure to force makeup fluid in through one of the check valves L or L to replenish fluid which is leaking from During the high pressure strokes of the pump and motor plungers all pressures be tudinal axis of the corresponding plunger during relative reciprocation between the plunger and corresponding track 13' or B". By this arrangement the rollers of each set reactnunder the transmitted plunger thrust to maintain the associatedcrossh-ead parallel with the corresponding track B or B and to maintain the line of thrust, which corresponds to the longitudinal axis of the plunger substantially normal'to the track. Vere the rollers of the set permitted to pass beyond this longitudinal axis or line of thrust the associated crosshead would 'tilt and the end thereof be forced against the adjacent lug C or C g As each set of rollers travels back and forth between its track and plunger crossiead the transmitted pressure is distributed between the rollers in different proportions, inversely as the distance from the plunger to the roller contact with the crossheadi This'is illustrated in Figures 15, 16 and 17.

Figure :15 shows the relationof the parts when the plunger axis interceptsthe axis of rotation of the driving disc and the crosshead is in central position The plunger thrust is then delivered equally to the two jrollers, but no driving torque is caused in driving disc B? by the plunger thrust. As-

suming a maximum eccentricity E of -1/2' inch, and the distance between roller centers 5/4inch, Fig. 16 shows the relation of parts when the plunger has translated l/ tinch away from the disc'axis. The roller cage plunger thrust of 1000 pounds, the figure shows that the rollers are now'bearmg respectivel 400 pounds and 600 pounds.

Figure 17 shows the furtherchange when has traveled 1/ 8 inch, and assuming a total by. which cylinder barrel 0 is carried,

aroundon the stationary pintle by the fit of the plungers in their respective cylinders.

This is accompanied by a slight additional modification of the loads on rollers B, but

still is accomplished without bringing cross head B in engagement with guiding lugs B. It will be understood thatthe only resistance to the revolution of cylinder barrel in Figure 17, and that the friction occurs immediately under that plunger, the moment of the frictional drag against the cylinder barrel C will be friction force multiplied by the radiusR of the pintle.

To overcome this drag, plunger B develops another force couple consisting of equal opposed forces C near 1ts lower and upper contact points, multiplied by the distance D between these points.

The pluilger, by means of the. crosshead on which it is mounted in turn delivers a third force couple of equal moment to the rollers B". One force of this couple increases the corresponding roller load by the amount C multiplied by D while the other force decreases 1ts -c0rre- D s'ponding roller'load by the same amoppt.

The peculiar form of the ports and coacting surfaces in the interior of the cylinder barrel C or C .and on the exterior of the pintles C or C further contributes to reduction of friction and increase of efficiency. Two'drainage portsor grooves H, H (see Fig. 10) and H H extend around the interior bore of the cylinderbarrels C and C respectively. The cylindrical contact surface included between the inner edges of these ports is subjected to the action-of high pressure on the pressure port side of pintle where the ad acent cylinders are filled with 'highpressure oil. .Around the semi-circle adjacent to low pressure port this surface is subject only to the action of low pressure oih Should a lifting'tendency exist it would beopposed and lifting prevented-by ,the action of the surface in con tact on the opposite side of the closely fitted valve pintle, which would not permit the port surfaces and valve face surfaces at any point of the circle to separate.

The cylindrical pintle surfaces outside of the grooves H, H, H? or H" have a double function,they close the grooves and make themact as leakageducts as hereinafter ex-, plained; and they also act as additional bearing surface forv the revolving cylinder barrel upon the valve pintle. In addition to these ducts the interior of each cylinder has cut around it near the outer end of the bore, drainage grooves H and H respectivelywhich communicate with the grooves H H respectively by passage H H.

Drainage grooves H and H also surround the counter pressure areas in the upper and lower gibs C and C respect vely. These gibs are also respectively provided with closed pressure chambers C" and C supplied respectively through the ducts "C" and G whith communicate respectively with the ports 0? and C thus insuring at all times the pressure chamber in each gib shall be supplied with oil of the pressure existing inthe corresponding port. As this pressure is also the pressure existing in the P p 7 of the cylinder barrel against the; pintle C, it follows that thisreactiontogether with the simultaneous reaction of cross rail 0 against, C, and the hydraulic counter pressure of gib against the cross rail G are always in proper relation to each other, as diagrammatically indicated in Figure 9,

without regard to the intensity of the oil pressure.

oyirinders C which cause the reaction Similarly, the zoneof contact at the sliding face between sliding pintle block OK asand. stationary cross rail C is divided by a groove H entirely surrounding the two.

ports (1, G into an inner area and an outer area. Either the upper or the lower half of the inner area, surrounding respectively port C or port C", is subject to high pressure. The other halfis simultaneously subject to low pressure. When the upper ports C C are under pressure, the oil i-sconfined by the oil seal surfaces'C (shaded horizontally) andthe central bar C (left blank) some oil graduallyleaking past the seals G into groove H and some leaking across the central bar C directly. into the low pressure ports 0 C The low pressure oil in ports C 0 is confined by the seal ,surfacesC (shaded vertically) inside of groove H and oil collected in this groove from leakage at this or'oth'er points is returned to port 0" by means explained later. When motor is reversed, ports C",

etc., and C", etc., interchange their above I described functions. a

When upper ports C, C, C and C are acting as pressure ports totransmit to the motor high pressure fluid delivered from the pump, the upper halves of the cylindrical pintle surfaces C C are subjected 'to-the high or Working pressure existing in the communicating cylinders. This pressure is confined'as closely as ossible by the oil seals or contact surfaces and C towards the outer ends of the respective p1ntles and C and C toward the inner ends of the respective pi'ntles. These surfaces are in working contact-and some oil under pressure gradually learhsfiast them into the drainage grooves H H and H"' Each of these four drainage grooves is connected by two-ducts H H, H and H re spectively withfour main leakage collect- 1 ing ducts H H in sliding block C and pintle C and H and, H in stationary cross rail- C and pintle C These main ducts lead directly into the rectangular groove H both from the pump pintle C and from the motor-pintle 0 thereby receiving all of the primary or high pressure leakage past the oil seal surface on the sliding pintle block C as already described.

The pressure existing in port C is also simultaneously conducted through the duct C intothe closed pressure chamber C in the upper gib (D -where it produces the hydraulic counter-pressure already described. Some oil leaks from this pressure chamber past the, oil seal surfaces C and C9 in the upper and lower gibs C and C respectivel into rectangular drainage grooves H and vtively. These grooves are always connected by the ducts H and H with the maincollecting ducts H and H wherebyany leakage across the gib oil seal surfaces'C or C is'returned into said main collecting ducts.

The ducts H and H together with all of the tributary. ducts already described,

form a closed system for gathering all of the oil which leaks past the aforesaid oil seal surfaces subjected to high. pressure. The primary orhigh pressure leakage \thus gathered is returned through one or other of the ducts H through check valves C or C -to whichever of the ports C or C is for the moment subjected to low of return pressure. This duct system, therefore, acts to return automatically and without pumping also without permitting escape into the open casing the principal part of the leakage past high pressure oilseals and working surfaces. 2

' A certain amount of oil, however, escapes "into the casing A passing the contact surfaces outside of the various drainage ducts already described; These contact surfaces of these secondary oil seals are subjected only to lower return pressure, and for reasons later described this pressure is prac tically constant, .without regard to the pressure existing in the high pressure portsto furnish necessary power to drive the motor.

' Therefore the amount of leakage escaping past these secondary oil seals into the easing A is practically constant under all con ditions and can be handled by a leakage return system of small capacity. Onthe other hand the leakage gathered in the systern of primary ducts already herein described and automatically returned thereby is large, because of the relatively high pres-,

sure, and variable because of the great variations in the working pressureexisting in the high pressure ports.

3 of the upper and lower gibs respec- I into the ports C or C pointed toward the pump intake or ports'C This secondary leakage escaping into the casing A and a catch basin A is returned by atmospheric pressure acting onthc inlet.

opening of one of the check valves L or L 1 .These valves are on the ends of the tubular extenslons of the ducts L and Ltfo-rmcd 1n the-sliding block C and communicate re- .port C and if this pressure -falls below the pressure of the atmosphere, due to lack of sufiicient return oil in lower port system to fill the suction spaces under the pump plungers, air pressure on the surface of the 011 body in catch basin A will forceun through the check valve L and duct L the necessary amount of make-up oil to fill the vacancy in the lower pressure port, and permit the pump to operate always with cylinders. full of oil. The atmospheric pressure is assisted. and a higher pressure maintained in low pressure ports by the action of the injector nozzles L and L through one ofwhich the returned leakage is discharged and C so that the rushof oil in themain ports passing the ends of the nozzles L and L sets up a suction in said nozzles. The nozzle happening to face the pressure port has the check valve {of its correspond-- 'ing duct L? (or L closed in consequence of said pressure and in this way the fluid is prevented from escaping back to the catch basin A. j

The relation between the currents of oil flowing in the main ports and these nozzles is indicated by the full arrows and by-the dotted arrows on Figure 3. With the pressure in the .upper ports C and C the flow will be in the direction of the plain'arrow impinging directly against the. mouth of the nozzle'L while the return flow through port C and C will be in the direction of the dotted 'arrowflowing past theopen end of the nozzle L". In this condition is the nozzle through which leakage must return and the suction generated by: said flow favors this. action. If the machine be reversed port C and 6" becomes the pressure port and the pressure flow is in the direction of plain arrow impinging against the mouth of nozzl L (The check valves L? or L close the ducts L or L against passage'of oil "as here'nbefore mentioned I when said oil is flowing as per plain arrows). The return flow is now in the direction. of dotted arrow and tends to assist by suction the entrance of returned leakage through nozzle L, the check valve L at the end of this duct L being now open. The suction head caused by the injector nozzle-is added to the available The nozzles are 1,4saeaathe returning working fluid as it rushes past the injector nozzle, increases the injector feed when it is inost needed to overcome the increased internal friction due to higher speed of liquid through the main ports, thus enabling the machine to operate faster before, reaching the limiting speed at which fteferring to Fig. 9 the arrow the devices for returning the secondary leakage into the main circuit become insufficient, and beyond which speed the machine cannot operate. a v

The catch basin A is formed by the outer walls of the main casing and by central inner partition A which is formed so as to' closely follow the periphery of the driving discs B and B During the o eration of the machine there is a continua escape of oil into the casing A past the plunger fits, etc. Part of this oil is thrown outward against the walls and drains directly down into the catch basin at the inlet openings A. I The remainder of the leakage seeps into the concave surfaces above the partition A, where it is wi ed up by the edges of the driving discsuan thrown against the vertical walls of the casing A, and drains down through the openings A?,' into the catch basin A". All of the leakage into the casing'is continuously returned to the catch basin A and thence byatmospheric pressure through the make-up check valves L or L back into the system. k

While in the catch basin, the oil is comaratively quiet, and the sediment collected is permitted to settle to thebottom, so that the returning oil which is taken from a higher level throu h the *check valves L, L willbe repeate ly clarified.

a d indlcates the total vertical reaction of the cylinder' barrel upon the pintle C the arrow. ab represents the reaction of the cross rail: against the gib C, which is formed with the slope necessary to receive this reaction a-b at right angles to its surface; and the" arrow a-f represents the consequent horizontal thrust of the crossrail against the sliding block, which thrust maintains a tight joint at the junctions of the sliding ports C and C with the stationary port-s C and C The arrows 0' (Fig. 10) indicate the counter pressure of oil between the bearingsurface of cylinder barrel against intle, tending to oppose the reaction The sev-' eral arr ws 0" represent the similar Oll counter pressure at gibC opposing the force a-b. The arrows 9 represent the similar oil ounter pressure at abutting faces of slidin pintle block C" and stationary cross rail G opposingthe force a-f.

The ducts and pressure chambers whereby these counter pressures are mamtained, m-

the respective gibs and the action of leak-v small pressure arrowslettered e 0" and g in Figure 10. As already explained, the abutting surfaces in each case are so limited by a system of drainage grooves that the oil counter pressure cannot become great enough to part the surfaces. In each case, therefore, thereis a small excess of mechanical pressure over hydraulic counter pressure represented by the greater lengths of the arrows ali, a-b and (II-f in Figure 9. The remaining forces d-e,

bc and f-g are sufficient to maintain mechanical contact, yet with greatly reduced friction. This permits the cylinders to revolve on their pintles, under heavy oil pressure but with slight frictional losses, and also permits the sliding pintle block to be moved as required to changethe speed of the motor, and without excessive efl'ort on the part of the operator.

When the pump is delivering liquid un-. er pressure, eac h' cylinder connected with the pressure ort is. delivering a large 'radial force against the pintle C, as indicated by the arrows in the upper'semi-circle of Fig. 11. The horizontal components of all of these axial forces largely cancel each in the same direction as indicated by the .small force triangles drawn in Fig. 11 on theaxes of the two inclined cylinders. The sum of all of these vertical components therefore acts downward- (or upward in case, of reversed motion) on the valve pintle C. a

This sum-of vertical components is represented by the line (i win Fi 9, and by the arrow d in Figure 10. Tt isequili- 'brat'ed by the horizontal force f of Figure 10, which represents the pressure of the ported face of the stationary cross-railC against the abutting ported face of the sliding block 0 and stationary cross rail C and by the inclined force b 'of Figure 10, ,which represents the total reaction of the In this operating condition, .the stationary cross rail is supporting the sliding block against the cylinder, reaction by the two other, but .the vertical components all act x stationary cross rail C against the gib C 2 forces f and b, the latter force reacting entirely against the gib C, while gib C? does-not carry any part of the load, and might fall away from contact with its cor responding gib surface and thus cause air leakage if it were not closely held in contact by springs P acting'on plungers P as illustrated in Figure 3.. The liquid under ressure in ports C and C acting against t e area limited by the upper half of the perimeter of drain groove H and by cross bar C in Figure 13 tendsto force apart the abutting ported surfaces between C and C and this counter pressure area is so proportioned that the hydrostatic force tending to separate the surfaces is somewhat less than the mechanical reaction f tending to hold them in contact. The mechanical force 7 therefore overcomes the hydrostatic foree, contact is maintained and leakage prevented, except such as is necessary for lubrication. At the .same time the mechanical friction to be overcome by the operator in the process of sliding the block 4 C7 to change the stroke is greatly reduced.

Similarly, the counter pressure area Within drain groove H in gib C (or C respectively) is so'proportioned that the hydrostatic pressure therein produces a force opposing and slightly less than the mechanical reaction bthus ermitting the mechanical" force to hold t e surfaces in contact with but slight leakage and greatly reduced friction, all in accordance with previous explanation referring to Figure 9. The pressure to which the surface adjacent to any cylinder port may be subjected depends upon the pressure within that cylinder,

ing the net area of the cylindrical surface located between the inner edges of the grooves H exactly equal to the .total cross sectional area of all of the cylinders, provided that the pressure per square inch in that part of the pintle surface 0 posite to the interior of any given cylin er is the same as the pressure inside of the cylinder;

but the pressure in this portion of the pintlef surface has an average value less than that in the interior of thecylinder because of the leaka e into the-grooves H which lowers the va veface pressure near the leakage edges. The width between the grooves H may be such as to include a total valve sea-t pressure area slightly greater than the total cross sectional area of the cylinders.

' It is preferable, however, to make the total cylindrical valve seat area slightly less than sufficient to lift the cylinders away from their valve seats.

When pump cylinder barrel C is delivering a heavy reaction to its supporting pint-1e C, the resulting stress in the metal of sliding blockC may produce slight deflections which, if not compensated, would tend to loosen whichever of the gibs C C, respectively, might be located on the side opposite to the gib surface supporting the reaction, Should such a loosening or separation take place, the suction side of the pump would tend to draw in air in between the loosened or separated gib and its corresponding surface. In order to enable one of these gibs to support a heavy reaction without shifting from its normal position, and at the same time to keep the other gib (which may tend to loosen on account of the deflections) pushed tightly against its corresponding gib surface, an

adjustable screwand plunger mechanism isprovided, the parts of which are designated upon the enlarged head P of a plungerP which rests in a corresponding socket P": in the gib. The reduced diameter of pro ection P v leaves room for a spring P, which always tends .to push plunger P hard against its corresponding gib, thus at all times pushing the gib as far as possible against its corresponding gib surface, and mantaining a contact between the gib and the gib surface irrespective of any defiections which may tend to relieve it. On the other hand, when one of the gibs as C is supporting the entire pump reaction it forces. the plungers P up against the ends of the adjusting screws P thus supporting the maximum loads independently of springs P.

-We claim 1.1m a hydraulic transmission mechanism the combination of a support, a pintle block adjustable thereon, abutting faces -on said support and block, fluid passages in said support and block communicating through said faces, a piston and cylinder assembly subjected to the pressure of fluid in said passages and producing a thrust on said block, and opposed faces on said sup port and block, said. opposed faces being inclin'ed iri'a direction away from the line of said thrust and toward said passages thereby reactingunder said thrust to maintain said abutting faces in close conta t,

, bers communicating t rough said faces,

2. In a hydraulic transmission the combination of a support, a pintle block adjustable thereon, abutting faces on said support and block, fluid passages .in said support and block conu-minicating through said faces, a piston and cylinder assembly subjected' to the pressure of fluid in said passages and producing a thrust on said block, faces on-said block each inclined in a direction toward the other and away from the 3. In a hydraulic transmission the combination of a fixed member, a memberadjustable thereon, abutting faces on said members, fluid passa es in said mema iston and cylinder assembly subjected to the pressure of fluid in said passages and producing a thrust on said 'ad us-table member, a face on one of said members inelined' in a direction toward said passages and away from the line of said thrust, and a gib connected with the other of saidmembers and having an inclined face in close contact with said last namedface.

4. In a hydraulic transmission the com bina'tion of a fixed member, a member slidable thereon,- abutting faces on said members, fluid passages 1n said members communicating through said faces, a piston and cylinder assembly subjected '-'to the pressure of fluid in said passages and producing a thrust on said adjustable-member in either of two opposite directions, faces on. one of said members each inclined in a dition toward the other and awa' from the 7 line of said thrust, and. gibs sli ablyconnected with the other of said members and fluid pump and motor in communication, ad-

bearing against said inclined faces.

5. In a hydraulic transmission the com-- bination of a fixed member, a second member slidable thereon, abutting faces on said 7,

members, fluid passages in I said members communicatlng t rough said faces, a piston and cylinder assembly subjected ,to the pressure of fluid in said passages and pro r, ducing a thrust on said slidable member in either of two opposite directions; faces on one of said members each inclined in a direction toward the other and away from the line of said thrust 'ibs interposed between said last named faces and the other ofsaid members, and yieldable means for maintaining said gibs in close contact-with said last named faces.

6. In a h draulic transmission the combination of a pport,a block slidable thereon, abutting fa s on said block and support, fluid passages in saidblock and support communicating'through sald faces, a.

clined faces, gibs slidable upon said piston and cylinder assembly at one side of the plane of said faces'subjected to the pressure of fluid in said assages 'andproducing a thrust on said b ock, and opposed thrust sustaining faces on said block and.

adjustable means for sustaining'the thrust of one of them and for varying the stroke thereof comprising fixed and movable blocks, gibs carrie by one of said blocks and embracing said other block, inclined faces on said other block on which said gibs may slide, and means for introducing fluid under pressure between said gibs and faces to sustain pressure therebetween.

8. In a hydraulic transmission having a fluid pump and motor in communication,

adjustable means for sustaining the thrust of one of them and for varying the strokethereof comprising a thrust sustaining movable-block, gibs thereon, a'support extending between said gibs and having inclined faces on which said gibs may slide, and

means for introducing fluid under pressure between said gibs and faces to sustain pressure therebetween. I L 9. In a hydraulic transmission having a fluid pump and motor in communication, adjustable means for sustaining the thrust of one of them and for varying the stroke thereof comprising a support havin inaces, a movable thrust sustaining member supported b said gibs, and means for introducing gibs and faces to sustain pressure therebetween. i Y

uid'under pressure between said justable means for sustaining the thrustof one' of them and for varying the stroke thereof comprising stationary and movable blocks, gibs carried by one of them, the other having inclined faces upon which said gibs may slide, an open pocket disposed be tween each "gib and the face upon which it slides, means for introducing fluid under pressure into said pocket, and a bleeder groove surrounding said pocket for draining ofi' fluid which leaks from said'pocket. 11.-In a hydraulic transmission having a fluid pump and motor in communication,

adjutsable means for sustaining the thrust of one of, them and for carrying the stroke thereof comprising a stationar rail having I inclined faces at the upper an lower edges thereof, a movable block, gibs su port ng said block and slidable upon said aces, an

open pocket between each gib and the face.

upon which it slides for receiving fluid under pressure, and a bleedergroove surrounding said pocket for i'nterceptingand draining oif fluid which leaks from said pocket.

12. In a transmission a stationary block,

a gib resting thereu .011, a movableblock siipported by said gi a pumping member supported upon the movable block, a

'- counter-pressure chamber formed between -'said gib'and stationary block, and means of said stationary member, fluid passages'in said members communicating through said face, operating meanson said movable member subjected to the pressure of fluid insaid passages, and meanssubjected to the fluid pressure in said passages for retaining said faces vincontact.

14."In a hydraulic transmission having a mitt ng element rigidly connected with each pump, a reversible motor and two fluid passages connecting pump and motor, either of which carri es the -Working fluid outgoing from the pump, the other simultaneously carrying the workingfluid returning toward the'pump,'two leakage returir ducts, one in each of said fluid passage ,botli terminating in orifices directed substantially in the direction offlow toward the pump, and

means for closing that leakage return diict which enters the passage containing high a pressure Working fluid.

15." In a hydraulic transmission two-members rotatable about substantially parallel.

axes, one of said members having a series of radial cylinderbores, a series of crossheads reciprocating longitudinally in said other member, one opposite each bore, and a thrust transmitting piston reciprocating in each boreand rockablyengaged with the athacentcrosshead.

16. In a hydraulic transmission two members rotatable about substantially parallel axes, a groupofcylinders and cooperating pistons disposed radially of one of said members, and a series of crosslieads reciproeat ng longitudinally in said other member,

each crosshead extending transversely of one of said cylinders and rockably engaged with its cooperating piston to receive th thrust therefrom.

17.YI'n a hydraulic transmission two members rotatable about substantially par- 'allel axes, a series of cylinders and cooperating pistons, each extending radially-of one of said members, a series of crossheads assesses reciprocating longitudinally in said other membenand thrust transmitting means between each o:t said crossheads and one of said pistons permitting a rocking actiontlie'rebetween normal to th plane of rota-' tiononly. I

18. In a hydraulictransmission two members'rotatal ile about substantially parallel axes, one of said members having a seriesof radially disposed cylinder bores, a hollow piston in each bore, a; series of crossheads reciproeati ng longitudinally in said other member, and thrust transmitting. means rigcrosshead and rockabl erating piston. e 20. In a. hydraulic transmission mechanism the combination of a pintle,.a-series of piston and cylinder assemblies i'adiallydisposedabout said pintle, a member having a series'of reaction faces, one opposite each piston and cylinder assembly and extending normal to'the axis of'reciproeation thereof,

y engaging the coo cylinderassembly and adjacent face and rockably associated with said assembly.

21.111 a hydraulic transmission the-coinbination of a pintle, aseries of piston cylinder assemblies radially disposed about between said member and each of'said assemblies and extending substantially nor-' mal to the longitudinal axis of the associated assembly, and connections between each crosshead and the associated assembly permitting slight rocking action therebe- .tween.

February, 1918.

- "WILLIAM E. MA-KTIIE.

\Vitnesses for William E; Magic:

CHARLES J. SIMi:oN, I

, James F. DUFFY. 4 r

Signed at South Milwaukee, 'isconsin,

the 9th day of March, 1918. v

' \VALTER FERRIS.

W'itnesses for IV alter Ferris H. MUELLER,

Geo. H. RONDEAU.

and a crosshead between each piston and said pintle, a reaction member, a ci osshead Signed'at li1flalo,N. Y., this an as of i 7&5 transmission the com 

